Injector



y 1941; E. Y. GUTHMANN INJECTOR 4 Sheets-Sheet 1 Filed Nov. 12, 1938 All/E 5754/? W M a 4 a ,0 K x 45 1:; 4 i U \k m a I III. |||.v.. 1..

July 8, 1941.

E. Y. GUTHMANN Filed No v. 12, 1958' IVIIIIIIIIIIIIIIIIIIIIIIIIIW30:2???2:

INJECTOR f v i 4 Sheets-Sheet 2 July 8, 1941.

= E. Y. GUTHMANN Filed Nov. 12, 1958 INJECTOR 4 Sheets-Sheet 3 y 3, 1941- E. Y1 GUTHMANN 2,248,679

INJECTOR Filed Nov. 12, 1938 4 Sheets-Sheet 4 I776 PRESSl/EE Myra Patented July 1941 ENJECTQB 7 Claims.

This application is in part a continuation of my copending application Serial Number 72,635, which issued August 12, 1940, as Patent No. 2,211,058.

A principal object of the invention hereindisclosed is to provide an injector of the exhaust steam type of generally improved structural and functional characteristics.

More specifically, an object of the invention is to provide an injector of the stated type that shall be characterized by relative simplicity of mechanical structure and assembly, compactness of form and high functional efliciency.

Still more specifically, an object'oi the invention is to provide an improved injector ofthe stated type that shall be operative automatically to utilize steam from the exhaust source to the exclusion of the live steam at such times as the saidexhaust steam may be available in sufficient quantities to meet the requirements of-the injector.

Another object is to provide a device of the stated character wherein the control of all the fluids involved shall be accomplished automatically through the medium of a single movablemember affording a unified and exactly synchronized interregulation of the flow of the: fluids in the injector.

Still another object of the invention is to pro-.

utilizing live. or exhaust steam for forcing and.

heating purposes, and comprising also. within itself means for automatically controlling. and

regulating the water supply and for selectively controlling the how of steam from the different sources and to diiierent points, as hereinafter described.

A still further object is to provide an injector of the character setv forth in the preceding paragraphs the operation of which as regards starting and stopping may be controlled through the medium of a single manual control member, or at most through the medium of a. main and a single supplemental control member.

iii).

Fig. 2 is a'detached view in perspective ofone of the elements of the mechanism;

Figs. 3, 4 and 5 are, respectively, vertical sectional views illustrating the device in various positions of automatic adjustment;

Fig. 6 is a fragmentary View showing a detail of construction;

Fig. 7 is a fragmentary sectional view illustrating a modification within the scope of the invention;

Fig. 8 is a vertical sectionalview illustrating the invention asapplied to another type of injector;

Fig. 9 is avertical sectional view of the fluid supply means of a single line injector .made in accordance with my invention; i

Fig. 10 is a fragmentary View showing a detail of construction, and

Fig. 11 is a fragmentary sectional view illustrating a modification within the scope of the invention.

With reference. to Figure 1 of the drawings, the injector feed water heater therein illustrated comprises a casing l having ports 2 and 3 adapted for connection to sources of water and exhaust steam respectively. The casing comprises a flanged head 4 having a depending cylindrical extension or bushing 5 which projects downwardly into the interior of the casing and which terminates at its lower end in a tapered extremity 6. The bushing 5 is hollow and receives for sliding adjustment in its cylindrical bore a sleeve 1, said sleeve embracing a cylindrical duct 8. The lower solid extremity 9 of the duct 8 is secured in the tapered end 5 of the bushing 5 by means of a set,

screw 1 i, and the upper end of the duct projects through the head 4 of the casing and is provided with a union l2 by means of which the duct may be connected with a source of live steam. The upper end of the duct'B where it passes through the head :l is embraced by a bushing It, said bushing being threaded into the head and being secured in predetermined adjusted position" by means of a lock nut it. The inner end 'of'the bushing 53 forms an abutment for an upper spring seat is, and anti-friction bearings I6 are interposed between the seat l5 and'the opposed end of the sleeve. The seat I5 receives one end of a coiled spring H, which embraces the duct 8 and which seats at its lower end upon the sleeve I. said sleeve being provided at its upper end with an extended recess I8 for reception of the spring. The spring I1 urges the sleeve 7 downwardly into the normal position in which it is shown in Figs. 1 and 7, and the pressure of the spring against the sleeve may be regulated in obvious manner through the medium of the bushing I 3.

The sleeve I carries a transverse pin I9, the mid portion 20 of which is provided with an opening through which extends the duct 8. The outer ends of the pin I9 project through slotted openings 2I, 2| in opposite sides of the bushing 5, through apertures 22 in anvil elements 23, see also Fig. 2, which are fitted slidably in the slotted openings 2I of the bushin 5, and terminate in an outer sleeve 24 which closely embraces the enlarged mid portion 25 of the bushing 5 and which has at its lower end a tapered extremity 26 which surrounds the tapered extremity 6 of the said bushing. The anvils 23, as shown in Fig. 2, are shaped to conform to the cylindrical surfaces of the sleeves I and 24, between which they are closely confined with their flanged head portions 21 in engagement with the upper end surface of the sleeve 24. The pin I9 unites the inner and outer sleeves l and 24 and the anvils 23 into a unitary structure adapted for sliding adjustment Within the casing.

Intermediate its ends the sleeve 24 is provided with a section 28 of increased diameter forming a shoulder 29 which seats upon the upper end of a combining tube 3|, this tube being suitably mounted within the casing and extending downwardly through the area of the port 2 to terminate at its lower end in a tapered extremity 32. The shoulder 29 by seating upon the combining tube 3! limits the downward movement under the action of the spring I1 of the sleeve 24, and hence of the sleeve I to which it is attached as previously described through the medium of the pin I9. The lower end of the sleeve 24 fits neatly within the upper end of the combining tube 3I' and has formed thereon a shoulder 33, which preferably, in the depressed position of the sleeve 24. seats upon a reverse shoulder formed in the tube 3 I, as illustrated in Fig. 1. The port 2 of the casing I communicates with a chamber 34. the inner wall of which is formed by the tube 3|, and the said tube is provided around its circumference with a series of ports 35 which communicate with the chamber 34 and which are normally closed by the lower end of the sleeve 24, as illustrated. The tapered extremity 32 of the combining tube is provided externally with longitudinal ribs 36, and between these ribs with ports 31 which, conventionally. provide for overflow of water from the tube to the overflow or suction chamber 38.

Suitably mounted in the interior of the easing I within the area of the port 3 is a sleeve 33, the lower end of which is perforated. as indicated at M. and this sleeve also is provided with. an inwardly offset depending flan e 42, which may be similarly perforated if desired and which lies in proximity to the outer surface of the sleeve 24. The port 3 communicates with a chamber 43 which embraces the sleeve 39. and this chamber is in communicat on with the annular chamber 44 in the interior of the sleeve 39 through the apertures in the lower end of the said sleeve and the space between the flange 42 and the sleeve 24.

The tube 8 is provided with a port 45 which normally registers with the upper end of a port 46 in the sleeve I which extends from the inner face of this sleeve downwardly therethrough to the lower end. The ports 45 and 45 thus establish communication between the interior of the tube 8 and the chamber 41 formed between the lower end of the sleeve I and the lower end of the in terior bore of the bushing 5. From this chamber 41 a port 48 of restricted cross sectional area extends through the lower tapered end 6 of the bushing 5 to the outer surface thereof. The sleeve 1 is also provided with a port 49, which when the said sleeve is elevated, as hereinafter described, to a predetermined extent is adapted to register with and establish connection between a port 5I in the wall of the tube 8 and a port 52 in the bushing 5. This port is formed directly below the enlarged mid portion 25 of the said bushing and communicates with the chamber 53 formed between the lower end of the bushing 5 and the outer sleeve 24. Registration of the port 49 with the ports 5I and 52 thus establishes a direct connection between this chamber 53 and the source of live steam. It will be noted that the port 49 and the upper end of the port 46 are in substantial alignment, and that the upper end of the port 45 corresponds substantially to the lower side of the port 5|. The bushing 5 also contains a fourth port, 54, which when the sleeve I has been elevated to a predetermined extent establishes direct communication between the chamber 41 and the chamber 53.

The outer sleeve member 24 has in the Wall thereof a port 55 which is normally closed at the inside by the enlarged portion 25 of the bushing 5. This port 55, when the sleeve 24 has been elevated to an extent bringing the port 49 opposite the ports 5| and 52, registers with a port 55 in the bushing 5, which port communicates with the chamber 51 formed between the sleeve I and the upper side of the enlarged portion 25 of the bushing 5. The port 55 communicates at its outer end with the chamber 44, which as previously set forth is in communication with the apertures in the lower portion of the sleeve 39 and with the chamber 43 which communicates with the port 3. The sleeve 24 also contains a pear-shaped port 58, see Figures 3, 4 and 5, arranged to register in predetermined positions of the sleeve 24 with a port 59 in the bushing 5 communicating at its inner end with the chamber 51.

Also provided in the sleeve 24 is a circumferential series of ports BI which when the sleeve 24 occupies a normal depressed position as shown in Figs. 1 and 3 are closed at the outer side by the combining tube 3|. When the sleeve 24 is elevated to a predetermined extent, these ports GI establish communication between the port 3 and the chamber 53.

Insofar as described, the operation of the device is as follows: With the parts in the positions shown in Fi s. 1 and 3, it will be noted that the ports 35 and GI being closed, both water and exhaust steam are excluded from the combining tube 3|. Also exhaust steam if present in the chambers 43 and 44 is excluded from the chamber 51. The spring I! tends to hold the movable parts in the depressed positions. and the exhaust steam not only has no tendency to elevate these parts against the pressure of the spring I but actually exerts a pressure at the upper surfaces of the anvils 23 and the sleeve 24 tending to hold the moving parts in the depressed position. If, now, live steam is admitted to the duct 8, this steam passing 'to the chamber 41 through the ports 45 and 46 will exert pressure against the lower end of the sleeve 1 tending to elevate this sleeve and with it the outer sleeve 24 from the normal positions. 1 This elevation of the parts has two effects; first, it opens the ports 35 and establishes communication between the source of water through the port 2 and the interior of the combining tube 3!, and, second, it. eventually brings the port as into registration with the ports and 52 so that live steam will pass from the tube 8 into the chamber 53 and downwardly through the tapered lower end 25 of the sleeve 24 into the combining tube 3|. The eifect of this steam discharging into the combining tube 3! is to heat the water entering the tube 3| through the ports 35. It will be noted that the arrangement provides by selection of the number, location and size of the ports involved in the operation described above a thorough regulation of the iiow of live steam and water to the combining tube, and this factor, coupled with the simultaneous and unified control of the water and steam inflow, provides for delivery of these elements to the combining tube inaccurately controlled ratio to afford the most efficient, economical and stable operation. With a device of this character, it is unnecessary to have any means for independent control of the water from the source.

Attention is directed to the live steam lift chamber 4'! and the manner in which steam is admitted thereto. The drain port 48 is smaller than the supply port 46, this permitting a gradual increase of pressure in the chamber avoiding too sudden lift of the moving parts. The length of the lift is determined by the length of the port at in the direction of movement, and is definitely limited by the pressure-equalizing port 55, which as previously described is opened when the sleeve I has reached a predetermined elevation corresponding substantially to the length of the port 65. The port 5% functions to permit an escape of excess pressure in the chamber 4-! and precludes upward movement of the sleeve 1 under the action of the live steam beyond the limits of the port 45. Preferably this latter port is restricted towards its upper end after the manner illustrated in Fig. 6; so that as the sleeve '5' rises, the effective area of the port is gradually decreased. This gradual reduction in area of the supply port and the fact that the drain port 58 is eventually supplemented by the equalizing port 56 makes possible the maintenance in the chamber ll of an effective pressure substantially equal to the weight of the moving parts and the counter pressure imposed by the spring I], so that a definite line or lift level may be established.

The initial lift thus'eilected'by the live steam.

brings the ports 5| to a position at the top of the combining tube 5i, wherein an additional lift will effect the opening of these ports to establish connection between the port 3 and the chamber Also the initial lift as previously forth brings the port 55 into registration with the port 56, and thereby admits exhaust steam, if present in the chamber M, to the secondary lift chamber 5'1. If exhaust steam is present in suflicient quantity to further lift the sleeves l and24 against he pressure of the spring H and the counter exhaust steam pressure upon the moving parts, there results an immediate closing of the live steam ports 45 and ill and an opening of the ports El admitting the exhaust steam to the chamber 53. The device is so designed that when the supply of exhauststeam is such that the steam from this source is capable of assuming the water heating function, the live steam from theother source is automatically cut off, thereby conserving the live steam for other useful work and utilizing the waste exhaust steamfor the water-heating operation.

It will be noted by reference to Fig. 4, which shows the moving parts in the initial lift position effected by the live steam as previously described, that the ports 58 and 59! have been brought to a position in which they are about to register. This registration, occurring when the exhaust steam further elevates the moving parts, supplies exhaust steam to the chamber 51 continuously to the point of maximum lift, as shown in Fig. 5. When the port 55 clears the upper end of the enlarged portion 25 of the extension this port also admits exhaust steam to the chamber 5?. Preferably the port 58 is' of inverted pear-shape, as shown in Figs. 3, 4 and 5, so that there is a gradual reduction in the supply of exhaust steam to thechamber 5'? toward the upper end of the stroke, thereby throttling the admission of the exhaust steam to the chamber and precluding undue shock at the upper end of the stroke. In this secondary lifting of the moving parts by the exhaust steam, the ports 6| are opened to admit exhaust steam to the chamber 53, from whence it passes through the tapered lower end 26'of the sleeve 25 into the tube 3! for combining with the water admitted to this tube through the ports 35. In this secondary lift also, there is a simultaneous and automatic regulation of the flow of the water and exhaust steam as in the previously described primary lift employing live steam with the same attendant advantages.

It will be noted further by reference to Fig. 5 that the regulation of theexhaust steam ports during the secondary lift is effected in part by the overlapping of these ports with the enlarged portion 25 of the bushing 5. The extent to which in the extreme elevated position of the moving parts the ports 5| are closed may differ from. that shown in Fig. 5, it being possible by increasing or decreasing the travel in the upward direction of the moving parts to vary the ultimate areas of the ports 6! exposed for'steam admission or to completely close them. It is apparent that with this arrangement of ports it is possible to obtain a well controlled and regulated flow of water and exhaust steam to the combining tube calculated to afford the most eiiicient results.

If at any time the supply of exhaust steam fails or is reduced to a point where it is inadequate for the water-heating function, the device will automatically adjust itself for continued operation from the live steam source. Thus when the parts by reason of the failure of the exhaust steam move under the action of the spring I! toward the normal depressed position, the ports 6! are out oh" and the port 45 simultaneously returned to registration with the ports 5| and 52, admitting live steamto the chamber 53. The operation of the device may be discontinued en- Means is also provided for manually returning the moving parts to the normal inoperative position in the event that it is undesirable or inconvenient to momentarily check the supply of exhaust steam. This means comprises a plunger rod 62 slidably mounted in the head 4 and normally occupying a retracted position as shown in Fig. l. The lunger is arranged so that when depressed it engages the top of one of the anvils 23, so that by the application of an adequate force, the entire moving-part assembly may be forced down against the pressure of the exhaust steam into the inoperative position. When under these conditions the supply of live steam to the tube 8 is discontinued, the exhaust steam is ineffective to again elevate the parts, so that they remain in the inoperative position. In this respect, attention is directed to the shoulder 29 of the outer sleeve 24 which normally seats as described upon the upper end of the combining tube 3!. When so seated, the effective pressure area of the moving-part assembly exposed to exhaust steam is that provided by the top surface of the outer sleeve 24 and the anvils 23, the steam pressure upon this area tending to retain the parts in the normal inoperative position. If this area is larger than the lift area of the moving-part assembly exposed in the chamber 57, the exhaust steam, even though admitted to the latter chamber, will not be eifective to elevate the parts from their normal or inoperative position. The excess area subjected to counter pressure preventing the lift by exhaust steam under these conditions is neutralized by the pressure of the live steam in the initial starting chamber 31. When the sleeve 24 is elevated from the normal position, however, the shoulder 28 forms a lift area exposed to the exhaust steam, which also neutralizes a portion of the counter pressure area at the top of the sleeve. In every instance the total of the eifective lift areas exposed to the exhaust steam pressure when the moving-part assembly has been initially elevated must be in excess of the effective counter pressure areas exposed under these conditions to exhaust steam. While in embodiments of my invention such as shown in Fig. 1 the operation does not necessarily depend upon the function of the shoulder 29 as a supplementary lift area, this function of the shoulder may be utilized to advantage in other embodiments of the invention, one of which will be hereinafter described.

Attention is directed to the central tapered element 6 at the lower end of the bushing 5. It will be noted that as the sleeve 24 is elevated the space between this sleeve and the part 6 becomes progressively more restricted, such restriction having a throttling effect upon the steam, and particularly the exhaust steam, passing from the source to the combining tube. The shape and dimensions of this tapered part, therefore, constitutes one of the factors of control and regulation of the operating pressures, and may vary in accordance with the specific requirements. Attention is also directed to the channel or port 63 and the cook 64 associated therewith which provides a means for bleeding the condensate from the exhaust steam chambers.

From the foregoing description the application of the device as a feed water heater in connection with an injector for locomotive and other engines will be apparent. The heated water is delivered from. the combining tube to the forcing tubes of the injector'in well known manner, the

latter tubes being operated in the conventional manner from the live steam source. When used for this purpose, the device will operate automatically for all conditions under which an additional supply of water to the boiler may be required. If, for example, the locomotive is standing so that only live steam is available for the water-heating function, the device is capable of operating efficiently with steam drawn from that one available source. If the locomotive is moving and working steam, the device once started by application thereto of the live steam will automatically change over to the exhaust steam, which is available under these conditions. The device is automatically operative to deliver steam under conditions wherein the supply of exhaust steam is erratic, such for example as when the locomotive is intermittently stopped and started, or when in motion, the steam intermittently is being worked or not worked. This latter condition may prevail for example when the locomotive is drifting. Under these conditions the device will automatically change over from live steam to exhaust steam operation when steam from the latter source is available and will return itself to the live steam position during those periods when the exhaust steam is not available. Under any of these conditions, the device may readily be thrown into or out of operation by the operator as demanded by the water requirements. This extremely flexible range of automatic operation, which is a characteristic peculiar to my device, is made possible in large part by provision of the means for simultaneous control of water and steam operated by and subject to the pressure control of the steam from the exhaust source.

It is evident that the greater the pressure of the exhaust steam, the heavier will be the drain on the Water in the boiler. Under these condi tions of available exhaust steam at high pressures, the automatic regulation of the ports 35 as described above will afford an increased supply of water through the injector to the boiler, and thereby compensates for the excessive drain. It will be apparent also that while the heater is operating solely with live steam, opening of the ports 35 is considerably reduced, say to the minimum capacity of the injector but suificient to supply the required amount of water to the boiler under these conditions. As the exhaust steam becomes available, the device automatically adjusts itself to the increased drain upon the boiler, and under extreme conditions of drain will deliver water to the full capacity of the injector. This action materially helps the operator in maintaining a satisfactory water level in the boiler. Simultaneous control of the water and steam also contributes materially to the economical operation and stability of the injector as previously set forth.

It will be noted further that during those periods of relatively great exhaust steam pressure when the supply is in excess of that required for heating the inflowing water, there is provision for automatic throttling of the exhaust steam supply to the combining tube. Such a condition might prevail for example when the wheels of the locomotive slip on the rails under difficult haul conditions. The excessive exhaust steam pressure then elevates the sleeve 24 to a point where the normal areas of the ports 6| are reduced by ring 25 of the bushing 5 and creates a further throttling effect between the lower end of the sleeve and the extremity 6 of the bushing. At the same time the water ports 35 are given their maximum opening. This automatic regulation maintains a proper relation between the water and steam supplies and insures a continued efficient operation under the extreme conditions.

Particular attention is directed to the fact that the moving parts of the device are limited in effect to a single member or-unit consisting of the sleeves l and 24, the pin IQ and the anvils 23, and that the movement of this assembly or unit is in a straight line corresponding to the longitudinal axis of the device. As a result, the device is extremely compact and symmetrical and free from structural complications. In this arrangement, the ring 25 of the bushing con-v stitutes an important element. It forms a sealing partition between the live and exhaust steam sources in that it separates the secondary or exhaust steam lift chamber 51 from the live steam passing from the primary lift chamber ll through the ports El, 49 and 52 into the chamber 53. It constitutes in effect a solid abutment from the under side of which the live steam is directed downwardly toward the combining tube and against the upper side of the which the exhaust steam may react in the secondary lift operation.

In Fig. 7 of the drawings, I have illustrated a modified means for admitting the exhaust steam to .the chamber 51. In this instance the port 55 is eliminated and is replaced by a port 65 in one end of the pin 19a. This port communicates with a channel 66 extending through the pin and through the adjoining portion of the sleeve 1. It is apparent that with this arrangement exhaust steam when available is continuously supplied to the chamber 51. Under this condition, it is essential that the counter pressure surface at the upper end of the sleeve 24 shall be of greater area than the lift pressure of the sleeve 7 exposed to the exahust steam within the chamber 5']. In this modification, the function of the shoulder 29 of the sleeve 24 as a supplementary lift area is to be noted. This area must be sufficient in extent that when added to the lift area of the sleeve 1 exposed in the chamber 57 it will increase the total effective lift area to an amount exceeding the counter pressure area at the top of the sleeve 25. It has been previously pointed out that when the moving parts orccupy their normal inoperative positions, wherein the shoulder 29 seats upon the tube 3|, that this area is not available for lift purposes. Under these conditions, therefore, the preponderance of the counterpressure area through which the exhaust steam tends to hold the moving parts in the inoperative position will be effective for that piu'pose. When, however, the moving parts are elevated initially by the live steam as described, the shoulder 29 immediately becomes effective as a lift area and combines with the lift area exposed in the chamber 57 to elevate the movable parts in opposition to the counter pressure of the exhaust steam.

In Fig. 8, I have illustrated the application of my invention to another well known type of injector. The control and regulating mechanism in this case is essentially the same as that described above, and the corresponding parts are accordingly identified by the same reference numerals. In this case, however, the outer sleeve 24 is disassociated from the water source. The steam chamber 53 communicates in this case with a chamber 58 which embraces the Venturi tube 69 extending from the live steam inlet port 61.- The chamber 68 communicates with the inner relatively large end of a tube H into which the discharge end of the tube 69 extends. The tube H in this case is mounted in the casing for axial adjustment, and this adjustment is effected through the medium of a pin 12 secured in eccentric position on the cylindrical head 73 of a shaft 14. The pin as illustrated projects into a slotted recess 15 in the outer surface of the tube Ti. By rotating the shaft 75 by means of its handle 1'6, the position of the tube H with respect to the tube 69 may be varied. The water in this case is introduced into the draft chamber 71 and is combined in subsequent tubes (not shown) with the steam delivered from the chamber 68 and through the tube 69. It will be ap-1 parent that the principle of operation in this instance and insofar as concerns the apparatus forming the subject of my invention is the same as that described above in connection with the embodiment illustrated in Figs. 1 to 5, inclusive.

In addition to the functional advantages set forth above, a device made in accordance with my invention is characterized by its relative simplicity of construction and assembly and its relative dependability resulting from the superior design which provides in effect a single moving part at all times under full control and never subject to violent shocks or jars under normal operating conditions. Other advantages reside in the compact form of the device, the accessibility of the parts for inspection, and the relatively low expens of manufacture. Specifically, it constitutes a material improvement over the prior devices used for and in connection with exhaust steam injectors to supply a continuous flow of steam alternating between two sources, not only as a matter of function but also because with its relatively few parts it is capable of accomplishing results not heretofore obtainable from the relatively complex assemblies employed in the art prior to my invention.

With reference to Figs. 9, l0 and 11 of the drawings, the injector therein illustrated as an embodiment of my invention comprises a casing 31 having ports 82, 83 and 84 for admission of high pressure or boiler steam, exhaust steam and water, respectively. The port 82 leads to a chamber 85 in the upper end of the casing; the port 83 to an annular chamber 86 in the mid portion of the casing; and theport '84 to an annular chamber 81 at the lower end of the casing, this latter chamber being arranged for communication through interior ports 88 with a draft tube 89 mounted as hereinafter described in the interior of the casing.

The draft tube 89 is formed at the lower end of a sleeve 9| which has at its upper end an outwardly extending flange 92 seating on the reverse interior shoulder 93 of the casing at the bottom of the chamber 86. Seating upon the upper surface of the flange 92 is a second sleeve 94, which is threaded into the casing at 95 and which intersects the chamber 85; and the lower portion of the sleeve 94 which occupies the chamber 86 is perforated as indicated at 96 and functions thereby as a strainer for the exhaust steam which enters the casing through the port 83. It will be apparent that the draft tube sleeve 91 is clamped in place within the casing by the sleeve 9%.

Mounted in the upper portion of the casing interiorly of the sleeve 94 and projecting upwardly into the high pressure steam chamber 85 is a bonnet 91, this bonnet having an outwardly ex-- tending flange 93 which seats upon a shoulder 99 in the casing and which immediately overlies the upper end of the sleeve 34. This bonnet is clamped in place by means of a follower ring IOI which is threaded into the casing as illustrated. Threaded into the upper end of the bonnet 9! is a tube or nozzle I02, the threaded end of the tube extending beyond the outer surface of the bonnet and being engaged by a lock nut Hi3, and the tube I02 extends downwardly and centrally through the bonnet and terminates at its lower end at a point, in the present instance, opposite the chamber 87.

Confined between the tube I62 and the inner wall of the bonnet 91 and finding a slide bearing on both of these parts is a sleeve I04, and this sleeve extends downwardly through the chamber 86 and into the draft tube sleeve BI, and terminates at its lower end in a conical extension I05 which occupies a position within the draft tube 00. The lower portion of the sleeve I04 above the extension I05 closely fits the inner cylindrical wall of the sleeve 9|, and a beveled shoulder I08 at the inner end of the said extension I05 is adapted to seat against a reversely formed shoulder I! in the sleeve 9i immediately below the ports 88, thereby to normally and positively seal these ports as shown. The sleeve I04 is also provided with a shoulder I08 which is adapted to seat normally upon the upper end of the sleeve BI, the function of this shoulder being hereinafter described. It will be noted that the sleeve I04 when in the said normal position, as shown in Fig. 9, constitutes an inner sealing wall for the exhaust steam chamber 86. Below the shoulder I08 the sleeve I04 is provided with an annular series of ports I09, which ports in the normal depressed position of the sleeve, as illustrated, are arranged to overlap a corresponding series of ports III in the sleeve 9|, these latter ports giving access to an annular chamber H2 in the casing 8I which extends downwardly around the water chamber 8'! and at its lower end communicates through ports H3 with the space surrounding the lower end of the draft tube 09 and with the interior of a vacuum tube I I4 which embraces the extension 89 and extends below the terminal end of the latter. As illustrated, the upper cylindrical portion of the vacuum tube I I4 through which the ports II3 extend closely fits the inner wall of the casing BI, and is threaded onto the draft tube 89. The vacuum tube H4 terminates at its lower end in the interior of a combining tube II5 which seats against a shoulder I I 6 in the lower end of the casing 8| and into the upper end of this combining tube the vacuum tube is threaded.

The upper end I04a of the sleeve I04 which occupies the interior of the bonnet 91 has threaded therein a (one or more) stem III which constitutes a retainer for a coiled spring I I8. The stem II! and the spring IIB extend upwardly through an opening in the top of the bonnet 9'! and into the interior of a cylindrical casing II9, which in the present instance is integral with and extends upwardly from the top of the bonnet 91 through the chamber 85 and has at its upper end a reduced cylindrical extension I2I which passes through a suitably sealed opening in the cover Bla of the casing BI. The extension I2I extends beyond the top of the cover Bio and is threaded for reception of a nut I22. The extension I2I is hollow and is interiorly threaded for reception of a screw I23 which extends downwardly into the spring casing I I9 and against the top of an upper spring retainer I24 which is slidable in the casing and which engages in the upper end of the spring H8. The arrangement provides for adjustment of the spring to regulate the compressive force exerted thereby against the upper end of the sleeve I04, which force tends to resiliently retain the said sleeve I04 in the depressed position in which it is shown in the drawings.

Between the sleeve 94 and the bonnet 9'! is provided an annular chamber I25, the upper end of which communicates with a port I25 which extends inwardly through the wall of the bonnet, and the inner end of this port I26 is normally closed by the upper end I04a of the sleeve I04 when the said sleeve is in the normal depressed position as illustrated. The lower end of the chamber I25 is in communication with the exhaust chamber 80 through a port or ports I2'I formed between the lower extremity of the bonnet ill and the inner wall of the sleeve 94.

The bonnet 91 is provided at opposite sides with ports i2 8 and I29, the port I28 communicating at its upper end, through a port I3I in the upper threaded extremity of the tube I02, with the interior of that tube; and the port I29 communicating similarly with the interior of the tube I02 through a port I32 in the upper end or" the latter. The lower end of the port I28 is adapted to communicate with the upper end of a port I33 in the sleeve I04 when the latter is in the normal depressed position, the port I33 extending downwardly to an annular chamber I34 which is formed between an inwardly extending shoulder I35 on the sleeve I04 and a reverse 7 shoulder I30 in a flange I31 which extends outwardly from the side of the tube I02 and against the inner wall of the sleeve I04. From the bottom of the chamber I34 a small port I38 extends downwardly to the space below the flange I31 and to the interior of the tube I04. The lower end of the port I29, as illustrated in the drawings, is closed by the sleeve I04 when the latter is in the depressed position, and this sleeve I04 has in its wall a pear-shaped port I39, see Fig. 10, which is in line with and normally below the lower end of the port I29, so that when the sleeve I04 is lifted, as hereinafter described, the port I39 is brought into registration with the lower end of the port I29. The inner end of the port I39 communicates with an annular chamber I4I formed between the tube I02 and the inner wall surface of the sleeve I04, the upper end of this chamber I4I being formed by a flange I42 projecting from the tube I02 and fitting slidably against the inner wall of the sleeve I04; and the bottom wall of the chamber I4I being formed by the upper surface of the projecting flange I31 of the tube I 02. From the bottom of the port I30 a channel I extends downwardly through the wall of the sleeve I04 to the shoulder I35, thereby communicating with the chamber I34. In the lower end of the chamber I4I ports I43 extend downwardly through the flange I31 and establish communication between the said chamber MI and the interior of the sleeve I04 at the upper end of the space between said sleeve and the lower end of the tube I02.

Above the port I33 the sleeve I04 is channeled longitudinally to provide an elongated port I44 which is in line with the inner end of the port I28, and the upper end of the port I44 extends inwardly through the sleeve I04 to communicate at its inner end with an annular chamber I45 formed between the flange I42 of the tube I02 and the under side of the upper end portion I041: of the sleeve I04. As previously set forth, the port I26 is normally closed at its inner end by the said upper sleeve portion Ifida, but when the sleeve is elevated sufiiciently, the port I26 is connected with the port I4 2, and through this port with the chamber I55.

The lock nut IE3 at the upper end of the tube I92, in addition to its locking function, is adapted also to form a seat for a valve I46, which valve when closed, as shown in full lines in Fig. 9, prevents admission of the high pressure steam in the chamber 85 to the interior of the tube I62. The stem Id! of the valve I46 extends upwardly through the cover member 8Ia of the casing 8| through a suitable packing joint I48 in the latter. The valve I46 also has a depending stem I4 9 which extends downwardly into the upper end of the tube sea, the portion of this stem I49 immediately below the valve I46 being of a diameter less than the interior diameter of the upper end of the tube H02, and the lower extremity II of the stem I29 being of increased diameter and in the present instance (though not necessarily) neatly fitting the cylindrical interior of the upper end of said tube. The stem M9 has a transverse port I52 extending from one side of the said stem to the other, and 'a central port I53 which extends downwardly from the center of the port I52 to the lower beveled extremity I5I of the stem. It will be apparent, therefore, that when the valve I46 is elevated from its seat on the lock nut H33, live steam from the chamber 85 will be permitted to fiow past the reduced portion of the stem I 49 to the ports I 28 and I 29,

and also through the ports I52 and I53 into the upper end of the tube I02. An initial slight elevation of the valve M6 will permitlimited flow of the live steam to said ports, and when the valve M6 is fully elevated so that the lower end of the stem I5I is carried clear of the upper end of the tube I82, as indicated in broken lines in Fig. 9, there is permitted a substantially free flow of the high pressure steam to the interior of the tube I62 and also to the ports I28 and I29. Manual means (not shown) is provided for actuating the valve I 46.

In the normal operation of the device, the valve I46 is first elevated slightly from its seat to admit steam from the chamber 85 to the ports I28 and I29, and through the ports I52 and I53 as previously described to the interior of the tube or nozzle I02. The high pressure steam passing through the ports I28 and I33 to the chamber iii-2 has the effect of elevating the sleeve lo l to a position of initial lift, wherein the ports 88 are opened to admit water to the interior of the draft tube 89. The high pressure steam initially entering and passing through the tube N32 has a desirable priming effect upon the device. This initial lift of the sleeve valve I84 also brings the port I39 into registration with the lower end of the port I29, and admits high pressure steam to the chamber MI, and through the ports I43 to the interior of the sleeve IM, this steam passing downwardly to and through the coned lower end of the sleeve and combining with the water in the draft tube 39. Initial lift under pressure of high pressure steam cannot extend beyond the point where the shoulder I 35 reaches the level of the shoulder M'Ia which forms the bottom wall of the chamber I4 I.

It will be noted further that the steam entering the interior of the sleeve IM. through the ports I53 is permitted to pass through the ports I I39, or through a supplemental series of ports 509a in the sleeve I84, through the ports I II to the chamber I :2, and from this chamber through the ports I It to the interior of the vacuum tube IId, this component of the high pressure steam being condensed by the water jet and aiding in the formation of the vacuum required to develop the necessary high velocity of the water jet delivered, as hereinafter described, by the injector. It will be noted that the two series of ports 59 and Iiiil'a are so relatively arranged that one or other of these series of ports is in a position to establish communication between the interior of the sleeve Iild and the chamber H2, so that this connection is continuous regardless of the position of the sleeve.

Following the initial limited elevation of the valve I46 and the resulting prime operation, the operator elevates the valve I46 to its extreme position, as indicated in dotted lines, to thereby permit the free flow of high pressure steam to the tube Hi2 and to the ports I23 and I29.

The initial lift of the sleeve valve I94 as described elevates the shoulder Hi8 from its seat on the upper end of the sleeve 9i, and also brings the port I 34 into communication with the port 125, whereby exhaust steam from the chamber passing upwardly through the port I27 into the chamber I25 is permitted to flow through the ports IN and IM to the chamber hi5. If now the pressure of exhaust steam is sufficiently great, acting on the lift surfaces at the top of the chamber I l-5 and under the shoulder I98, to overcome the resisting and opposing forces including the pressure of the spring H8, the steam from that source will still further elevate the sleeve I24, thereby disconnecting the port I33 from the port I23, and the port I39 from the port I29. At the same time, this additional lift will carry the ports I99 into communication with the exhaust steam chamber 86, and will permit a direct flow of the exhaust steam from this chamber to the interior of the sleeve H3 3. Similarly, through the ports E6911 the exhaust steam will be permitted to pass to the chamber I52, and from this chamber through the ports Hi; to the interior of the vacuum tube H4. Thus the live steam previously passing into the interior of the sleeve 18d and through the chamber M2 to the vacuum tube H4 will be replaced by exhaust steam, which takes over the function of the high pressure steam with a resulting economy of the latter. The injector now operates on an exhaust steam basis, and this operation will be continued as long as the exhaust steam pressure is sufficiently great to maintain the sleeve valve IE5 in the elevated position. If the exhaust steam pressure is reduced to an extent permitting the sleeve to fall, the live steam is again brought into action to maintain the sleeve in the position of initial lift, wherein the injector operates solely on the highprcssure steam.

When the device is operating on the highpressure steam basis, it is only necessary, in order to discontinue the operation of the injector, to manually close the valve bit. If, however, it is desired to discontinue the operation of the injector when the latter is operating on the exhaust steam basis, it is necessary not only to close the valve Hi5, but also either to shut 01f the exhaust steam from the chamber 86 or to forcibly return the sleeve valve I04 to its depressed or normally seated position. For this latter purpose, I have provided at the top of the bonnet 9'! a plunger 1 54 which extends downwardly through an opening in the top of the bonnet and which is slidably housed within a cylindrical casing I55 extending upwardly from the top of the bonnet through the casing cover 8 Ia, this housing being similar in form and mode of attachment to the casing H9 previously described, but including in addition a suitable packing joint I56 through which the stem I51 of the plunger I54 extends. This plunger may be moved downwardly by manual means to engage the upper end of the sleeve valve I04 and to force the said sleeve downwardly to its normal depressed or seated position wherein the passage of exhaust steam from the chamber I16 through the ports I09 is prevented. It will be noted that I have provided in the plunger IM a passage or port I58 shown in dotted lines which extends longitudinally through the plunger to establish communication between the upper interior space 90 of the bonnet 97 and the atmosphere whereby the sleeve IE4 is permitted to move upward into the otherwise closed upper end of the bonnet,

and whereby also the exhaust steam operating on the lift surfaces of the sleeve valve Hi4, as previously described, may be effective to elevate the sleeve. Leakage of steam between the sleeve W4 and the wall of the bonnet 97 into the chamber 90 is largely prevented by packing ring I50, and by the further fact that high pressure steam from the passage I29 tending to leak between the sleeve and the bonnet wall may escape readily by way of the port I39 to the low pressure chamber l il; or in event that the inner end of the port I39 is blocked by the flange I42, the high pressure steam leakage may still pass freely to the chamber I il by way of the channel I40.

The channel Hill has a further valuable function in providing recoil action of the high pressure steam to eliminate undesirable inertia eifects in the movements of the sleeve ifl i. The component of the high pressure steam entering the channel exerts a reactionary lift force upon the sleeve which in amount depends upon the crosssectional area of the channel and the degree of restriction of the inner end of the port I39.

In Fig. 11 I have illustrated a modification which in effect increases the effective areas of the exhaust steam lift surfaces of the sleeve valve I04 with respect to the counter pressure areas of that sleeve. The construction is the same as that shown in Fig. 9, with the exception that the sleeve Hi l is of somewhat greater thickness above the shoulder I38, so that the effective area of this shoulder may be increased without, however, increasing the effective counter pressure areas. This arrangement renders the device more sensitive to operation by the exhaust steam fed to the chamber 86 as previously described. The principle of operation of the device, however, remains unchanged.

It will be apparent from the foregoing description that by this invention I have provided in a single compact unit an exhaust steam injector of the single-line type, wherein through the medium of a single movable member a fully automatic control and regulation is afforded, not only of the steam admission but also of the water supply, and wherein further the changeover from high pressure to exhaust steam operation, and vice versa, is eiiected automatically and directly in accordance with the ability of the exhaust steam source to supply the requirements of the injector. It is'to be noted further that by reason of the unified control of the water and steam admission, the device affords an automatic interregulation of the fiow of these two fluids to the injector, and this interregulation is such in the case of the exhaust steam as to automatically compensate for the unavoidable fluctuations in the pressure from the exhaust steam source. Thus when the exhaust steam pressure is relatively low and the sleeve valve i0 1 assumes an intermediate lift position, the effective area of the water admission ports 83 will be rela tively small, and when the pressure of the exhaust steam is relatively great and the sleeve valve accordingly takes a position of extreme lift, the area of the exhaust ports will be correspondingly increased to thereby synchronize the admission of water with the relatively great quantity of available exhaust steam. It will be noted further that in this device the various elements of the injector are arranged around a common longitudinal center line, and that the single moving element works along this line, so that all undesirable or detrimental side pressures and lifts are avoided. Attention is also directed to the fact that the admission of all fluids involved in the operation of the injector and in the automatic actuation, including also the high pressure steam admission to the tube I02, is controlled by the manually-operated valve element I48, and that by reason of the fully automatic control and regulation of the device as described, this valve member I46 constitutes the sole necessary manual control, with the exception only of the plunger I54, which, as previously described, is not required when the device is operating solely on high-pressure steam. and may, in fact, be eliminated in favor of a valve for controlling the passage of exhaust steam to the exhaust steam chamber 86.

In describing and illustrating my invention, I have disclosed only those portions of the injector which are necessary to a proper understanding of the invention, it being understood that beyond the vacuum tube l I 4 and the combining tube I 15, which are conventional elements of a steam injector of this specific type, the injector device will also include the conventional delivery cone and associated parts. It will be understood also that there may be considerable modification in detail of construction without departure from. the invention. While, for example, I have illustrated a single spring I l 8 for normally retaining the sleeve valve I04 in its depressed or seated position, there may be and preferably is a plurality of such springs arranged to afford an accurately balanced device, and the construction as illustrated obviously affords adequate available space for this purpose. It is to be noted further, for example, that the port I 53, the function of which is to admit a priming jet of high-pressure steam to the tube I02 when the valve I45 is initially elevated, may be eliminated, as this is not essential to the operation of the device, although desirable for priming purposes as described.

I claim:

1. In a steam injector the combination with a casing having a discharge opening and ports for admission of water and of steam from both high pressure and exhaust sources, a steam nozzle arranged for communication with said steam ports, and a draft nozzle arranged in advance of said steam nozzle for communication with the said Water port, a valve member movably mounted in said casing and operative with respect to said ports and constituting thereby a common means for directly controlling passage to said nozzles of the steam and Water admitted to the casing through said ports, means providing separate primary and secondary lift chambers between said. valve member and relatively fixed portions of the casing in which chambers fluid pressure may act to move the valve, means for initially connecting the said primary chamber 1 with the high pressure steam port to thereby move the valve to an initial lift position providing a passage for steam from the high pressure source to the steam nozzle and admitting water to the draft nozzle, means operative in said initial lift position of the valve to connect said secondary lift chamber With the exhaust steam port whereby the steam from the exhaust source may further lift the valve to admit exhaust steam to the steam nozzle and to close the said high pressure steam passage.

2. A steam injector having individual ports for admission thereto of water, live steam, and exhaust steam; a steam nozzle arranged for communication with said steam ports; a draft nozzle arranged for communication with said water port; a composite valvemember adapted to cover the said several ports to thereby prevent fiow therethrough of water and steam to said nozzles, and being movable to uncover said ports so as to afford a simultaneous flow of Water and steam to the respective nozzles; said steam ports being arranged with respect to each other and to the valve so as to afford a selective opening of said live and exhaust steam ports; means actuated by fluid pressure from the live steam source for moving the valve to an initial posion wherein water is admitted to the draft nozzle and live steam to the steam nozzle to the exclusion of exhaust steam; and means adapted for actuation by fluid pressure from the exhaust steam source for further moving the valve to a secondary position admitting exhaust steam to said steam nozzle to thev exclusion of live steam.

3. A steam injector comprising a main steam nozzle; a draft nozzle; individual ports for admission of live and exhaust steam respectively to said steam nozzle; a port for admission of water to the draft nozzle; a composite valve member directly operative on all of said ports for controlling and regulating admission therethrough to the respective nozzles of water, live steam, and exhaust steam; a supplemental steam nozzle; manually-operated valve means for controlling the passage of live steam to said supplemental nozzle and to the said live steam admission port; means operative automatically upon the opening of said manual valve for moving said composite valve by fluid pressure from the live steam source to an initial position Wherein the live steam is admitted through said admission port to the main steam nozzle and water to the draft nozzle while excluding exhaust steam from the said steam nozzle; and means operative when the composite valve is in the said initial position and by fluid pressure from the exhaust steam source to further move the composite valve to a secondary position wherein the said live steam admission port is closed and the said exhaust steam admission port is opened to admit exhaust steam to the main steam nozzle.

4. A steam injector comprising a main steam nozzle; a draft nozzle; individual ports for admission of live and exhaust steam respectively to said steam nozzle; a port for admission of water to the draft nozzle; a composite valve member directly operative on all of said ports for controlling and regulating admission therethrough to the respective nozzles of water, live steam, and exhaust steam; a supplemental steam nozzle; manually-operated valve means for controlling the passage of live steam to said supplemental nozzle and to the said live steam admission port; means operative automatically upon the opening of said manual valve for moving said composite valve by fluid pressure from the live steam source to an initial position wherein the live steam is admitted through said admission port to the main steam nozzle and water to the draft nozzle while excluding exhaust steam from the said steam nozzle; means operative when the composite valve is in the said initial position and by fluid pressure from the exhaust steam source to further move the composite valve to a secondary position wherein the said live steam admission port is closed and the said exhaust steam admission port is opened to admit exhaust steam to the main steam nozzle; and means for returning said composite valve to a position closing said water admission port.

5. A steam injector comprising a main steam nozzle; a draft nozzle; individual ports for admission of live and exhaust steam respectively to said steam nozzle; a port for admission of water to the draft nozzle; a composite valve member directly operative on all of said ports for controlling and regulating admission therethrough to the respective nozzles of water, live steam, and exhaust steam; a supplemental steam nozzle; manually-operated valve means for controlling the passage of live steam to said supplemental nozzle and to said live steam admission port; and fluid-pressure means operative automatically upon the opening of said manual Valve for actuating said composite valve by fluid pressure from said live and exhaust steam sources to effect a controlled and interregulated flow of steam and water to the said main steam and draft nozzles, said fluid-pressure means comprising pressure chambers operatively associated with said composite valve for live and exhaust steam respectively in which chambers said steam is operative to shift the said valve; means operative when said manual valve is opened for admitting live steam to the first of said pressure chambers to thereby shift the composite valve to an initial position admitting water to the draft nozzle and live steam through said admission port to the said main steam nozzle; means for limiting the extent of said initial shifting of the valve by the live steam; means operative in said initial position of the valve to connect said secondary lift chamber with the exhaust steam port whereby the steam from the exhaust source may further shift the valve beyond said initial position; and means for interrupting the flow of live steam through said admission port and for admitting exhaust steam through the exhaust steam admission port to the main steam nozzle when the composite valve is shifted by exhaust steam pressure beyond said initial position.

6. A steam injector comprising a main steam nozzle; a draft nozzle; individual ports for admission of live and exhaust steam respectively to said steam nozzle; a port for admission of water to the draft nozzle; a composite valve member directly operative on all of said ports for controlling and regulating admission therethrough to the respective nozzles of water, live steam, and exhaust steam; a supplemental steam nozzle; manually-operated valve means for controlling the passage of live steam to said supplemental nozzle and to said live steam admission port; and fluid-pressure means operative automatically upon the opening of said manual valve for actuating said composite valve by fluid pressure from said live and exhaust steam sources to effect a controlled and interregulated flow of steam and water to the said main steam and draft nozzles, said fluid-pressure means comprising pressure chambers operatively associated with said composite valve for live and exhaust steam respectively in which chambers said steam is operative to shift the said valve; means operative when said manual valve is opened for admitting live steam to the first of said pressure chambers to thereby shift the composite valve to an initial position admitting water to the draft nozzle and live steam through said admission port to the said main steam nozzle; means for limiting the extent of said initial shifting of the valve by the live steam; means operative in said initial position of the valve to connect said secondary lift chamber with the exhaust steam port whereby the steam from the exhaust source may further shift the valve beyond said initial position; means for interrupting the flow of live steam through said admission port and for admitting exhaust steam through the exhaust steam admission port to the main steam nozzle when the composite valve'is shifted by exhaust steam pressure beyond said initial position; and pressure means acting on said composite valve in opposition to said steam pressures and tending to return the said valve to the normal position of admission-port closure.

7. A steam injector comprising a steam nozzle; a draft nozzle; individual ports for admission of live and exhaust steam respectively to said steam nozzle; a port for admission of water to the draft nozzle; a valve member operative with respect to said ports and constituting thereby a common means for directly controlling passage to said nozzles of steam and water through said ports; means providing separate primary and secondary lift chambers in operative association with said valve member in which chambers fluid pressure may act to move the valve; means for initially connecting the said primary chamber with the live steam port to thereby move the valve to an initial lift position providing a passage for steam from the live steam source to the steam nozzle and admitting water to the draft nozzle; and means operative in said initial lift position of the valve to connect said secondary lift chamber with the exhaust steam port whereby the steam from the exhaust steam source may further lift the valve to admit exhaust steam to the steam nozzle and to close the said live steam port.

EUGENE Y. GUTHMANN. 

